TD 491 
.P7 
Copy 1 



T D 




LIBRARY OF CONGRESS. 



Chap. __ Copyright No. 

ShelfDD....^ ^ I 

UNITED STATES OF AMERICA. 



Catalogue of, 

IbiQb pressure Ib^&raulic 

ittings * and * Flanges 

. , ffoll^*6 ipatent . . 
auD^ 

IFntormation for mae In DesiQuino 

^Rydraullc* Plants «« 





CATALOGUE OF 

HIGH PRESSURE HYDRAULIC 

FITTINGS AND FLANGES. 

(folly's patent.) 

AND 

INFORMATION FOR USE>' IN DESIGNING 

hydraulic/plants. 

john'^latt, 

MEMBER OF THE AMERICAN SOCIETY OF MECHANICAL ENGINEERS^ 
AND ASSOC. M. INST. C. K. 



m 










\^\ u^" ^--^r 



"TIGHT JOINT" FLANGE. \ 



Tio-xacrr toii^tt 



; AUfitS1896 



159-161 BANK STREET, 



HlUV$)'^ 



^ 




f 



<^% 



Copyi-ight. 1^96. 

BY 

TIGHT JOINT COMPANY. 
New York. 



im^ 



PREFACE. 



In the following pages it has been our aim to place before 
the hydraulic engineering world particulars of our well- 
known ''Tight Joint" and its adaptation to fittings and 
flanges specially designed to suit their needs. 

We are glad to be able to report that engineers can now 
procure fittings and flanges that will insure their being able 
to make tight joints, and that the trouble and annoyance of 
leaky joints they have heretofore had to contend w4th, can be 
obviated by the use of our specialties. 

For the compiling of the ' ' Information for use in designing 
Hydraulic Plants " we are indebted to Mr. John Piatt, the well- 
known high pressure hydraulic engineer, of 97 Cedar St., New 
York City. Much of the information is taken from notes col- 
lected by him, both in this country and while associated with 
Mr. James Piatt, Member of Council of the Institute of Mechan- 
ical Engineers, who has done so much to further the develop- 
ment of high pressure hydraulic machinery, A number of 
the tables have been specially conipiled and others taken from 
Mr. William Kent's ''Mechanical Engineer's Pocket Book," 
Mr. Henry Adams's "Hand-book for Mechanical Engineers." 
and other engineering note -books. 

We trust that the information given will be found of benefit 
to those who undertake the designing of hydraulic machinery, 
and we shall be glad if its users will kindly draw^ our attention 
to any errors of omission or commission, and also make any 
suggestions that may tend to make the '* Information " more 
valuable. 



ERRATA. 



l\ige 27, 

Table of W. I. & S. pipe 
should read, 

No. of til reads per inch, 
48 

18 

14 

14 

llt^ 

lU 

IH 

ili^ 
8 



Faxje 37. 

Capacities of Cylinders. 


Diani. 

Inches. 

18 

1 


Load at 
1500 lbs. 

199050 



Page 3Jf. 

Thickness of cylinder 
should read, 

Rankine gives. 

VAs~+~p 
X r 
s — p 

Page 39. 

Seventh line from bottom 
of page should read, 
. Efficiency per cent. 

80 ' 76 72 

Page 41. 

Thirteenth line from to]) 
of page should read, 

V pipe reduced to f " at one 
point. 

Formulae for areas of 
valves should read, 

W = Weight of ram, &c. 
Page 43. 
Formula should read, 
w k'- f m 
a = — 



PART I. 

HIGH PRESSURE HYDRAULIC 
FITTINGS AND FLANGES. 

(Folly's Patent.) 



Description of Tight Joint Hydraulic 
Fittings and Flanges. 



•' Tight Joint " fittings have established such a reputation 
for ammonia work, and proved so very satisfactory under the 
heaviest pressures obtainable, that we have decided to manu- 
facture a line of Standard High Pressure Hydraulic Fittings 
and Flanges, making use of the best hydraulic experience of 
this country and England. 




(1) SECTIONAL CUT OF FITTING. 

The ''Tight Joint" itself will be readily understood from 
Figure 1 , and the following description : 

The pipe is screwed into the fitting as in the case of ordinary 
low pressure work, and does not butt against a shoulder. The 
joint is made by means of a lead collar 1-4 in. wide by 3-16 in. 
deep, cast in the fitting three or four threads from the end. 

.7 



8 



TIGHT JOINTS. 



Holes leading into the recess are tapped for 1-4 in. set screws. 
one or more set screws being used, according to the size of the 
fittings. The lead collar is formed on a mandrel of slightly 
smaller size than the fitting, so that the lead is left projecting 
a very little beyond the threads. If a pipe be screwed into 
the fitting it will exj^and the lead packing, causing it to tightly 
fill the screw threads, and if the joint is not made tight by this 
means, one or more turns of the compressing screw will crowd 
the lead around the pipe and make it absolutely and perma 
nently tight. 

Malleable Iron. 




'TIGHT joint" coupling. 



Having described our system of making screwed joints tight, 
we will now look into the question of high pressure fittings 
and compare the old practice of making joints with our own. 

Two methods are adopted in generarpractice, the one de- 
pends upon screwing the pipe into the fitting so tightly that a 
leak cannot take place, this necessitates a perfect thread and 
also that very considerable force be used in screwing the pipe 
into the fitting, so much being necessary at times that 
it is no unusual thing to burst a fitting. The second method 
— a preferable one— is to let the end of the pipe butt against 
some material, such as leather or copper, and thus make a 
joint between the two pipes; in this case it is not necessary 
that tlie pipes be screwed so tightly into the fitting, but to 
insure a perfect joint under high pressure great care has to 
be taken in preparing the end of the pipe. In piping up a 
plant having a number of turns it is necessary that the pipes 



TIGHT JOINTS. 9 

shall be cut off absolutely to length; and in the case of 
flanges, in erection it is even necessary to take down one 
piece of pipe a number of times to alter the length so that 
the flange can be sci'ewed around to bring the boltholes in 
their proper position. 

Those who have had to do with piping up for high pressure 
will appreciate the difficulties they encounter in erection and 
will at once see the advantage they will secure from using 
our type of fittings. 

It will be seen from Figure 1 that in the case of the Tight 
Joint, as long as the edge of the pipe projects a quarter of an 
inch beyond the lead collar a perfect joint can be assured, 
hut the end of the pipe may be carried as much as f of an 
inch beyond this point. In this way a considerable latitude 
is possible and erection made very easy. 

As an example of what has been done in this direction with 
Tight Joints, we would refer to the piping for the High Pres- 
sure Hydraulic Elevator Systems in the Girard Life Building 
in Philadelphia and the American Tract Society Building in 
New York, put in by Otis Brothers Company. In the latter 
plant several hundred fittings were used, and some idea of 
the intricacy of the p'ping may be obtained from Figures 3 
and 4. 




txfl 


fcj) 


X 






Xi 


00 




'^ 


3 


o 


CD 


11 


>^ 








a> 








u 


c 


o 




CO 


nfl 




c 


o 


Q- 


OJ 


Q-h- 



CO 'k- 

^ E 

.E c 
o 



bn 
o 
■•-• 
o 

CL 



10 



fe','*^ ' ' A'-^vf^ 



k 




11 



12 TIGHT JOINTS. 

On testing these two plants (which carry a working pres- 
sure of 750 lbs.) not a single leaky joint was found 

A great many experiments have been made with the Tight 
Joint fittings and everything has been done that was possible 
to test their efficiency. 

Prof. D. 8. Jacobus, of the Stevens Institute, made a series 
of tests, and the following are some extracts from his report : 

•• i-incli and | inch Brass Tees — Made to leak and tighten 
lip at 800 pounds per square tnch steam pressure. 1.700 pounds 
})er square inch gas pressure, and 8.000 pounds per square 
inch iieavy refined petroleum oil pressure. 

•• 1 inch Iron Tee, No. 2. — Made to leak and tighten up at 
5.000 and 10.000 pounds crude petroleum oil pressure nnd 
5,000 and 10.000 pounds water pressure. Withstood 15,000 
pounds per square inch crude oil pressure withoiit leakage 
and 16,000 pounds water pressure. 

"1-inch Brass Hydraulic Tee, No. 2. — Made to leak and 
tighten up at 5,000 pounds per square inch water pressure." 

From these experiments it will be seen that it is possible by 
tightening up the small set-screw to compress the lead and to 
make it flow in such a manner that a leak at five or six thou- 
sand pounds per square inch can be taken up and a joint made 
perfectly tight without taking the pressure off the system. 

To sliow^ that expansion and contraction have no effect what- 
ever upon the joints we would refer to the following report 
made by Mr. Charles O'Connor, superintendent of the Pratt 
Works of the Standard Oil Company : 

" I have tested your fitting and find it to be in every sense 
just as you recommend it. The tests were made in the fol 
lowing manner: I built a coil of 2-inch pipe, using six (6) of 
your 2inch Return Bends, making 12 joints. On first test 
we found that at 800 pounds air pressure (under water) there 
were two small leaks, and by setting up one or two turns on 
set-screws they became tight. I was somewhat doubtful as 
to the joints remaining tight where there would be great ex- 
pansion and contraction, so I raised coil out of water and 
turned steam through it at 80 pounds pressure until coil was 



TIGHT JOINTS. 



18 



as hot as steam would make it, then I turned off steam, sub- 
merged coil in cold water and again applied 300 pounds air 
pressure and found every joint tight." 

That the working of a large hydraulic system during an 
extended period has no effect upon the joint has been proved 
by its use in High Pressure Hydraulic Elevators, Hydraulic 
Riveters, Presses, General Hydraulic Systems, High Pres- 
sure Steam, 1.500 per a " Air Pressure and a very extended 
use in all classes of Ammonia Work. 

All fittings and flanges are made of air furnace malleable 
iron having a tensile strength of from fifty to sixty thousand 
pownds per square inch. We do not use the so-called 
malleable iron poured from a cupola, and can thus insure 
fittings being sound and reMable. 

All fittings are tested by hydraulic pressm^e before leaving 
the works, as per table on page 3^1. 




(5) 



-f4'"""^^l't^-/i''-H 



'TIGHT JOINT FLANGE UNION5 



The flange unions are furnished complete with bolts and 
guttapercha rings. Single flanges, either male or female, can 
be used for connecting to valves or cylinders. The tables of 
flanges on pages 15 and 16 will furnish the dimensions neces- 
sary for engineers to design the details of their connections 
to suit the fittings we carry in stock. 



14 TIGHT JOINTS. 

The joint between the flanges is the * Armstrong " standard 
and made, preferably, witli a round guttapercha ring. This 
makes the best and most durable joint, though leather or lead 
can also be used for this purpose. 

Tlie threaded openings of the flange unions are made tight 
by the use of the " Tiglit Joint ' lead collar and set-screws de- 
scribed on page 7. Tlie combination of this device vrith the 
'* Armstrong " flange joint makes an absolutely reliable hy- 
draulic flange union. 

The foUowiiig tables give the standard sizes of Flanges for 
750 and 1 500 lbs. per square inch. 



TIGHT JOINTS. 



15 




)«5s^- ^-H 



Table of '^ Tight Joint*' Flanges. 
750 lbs. Working Pressure. 





A 


B 


c 


D 


E 


F 


G 


H 


K 


L 


M 


N 


o 


p 


Q 


R 


1 

Size 
of 




oS C8 

^ 5 


































Bolts 


^ 1 


i 


.84 


H 2i 


ii8i 


li 


If 


1 


1 


H 


A 


li 


i 


4 


lA 


f 


f 


1 


f 


1.05 


H 


2i 


H 


n 


li 


3 


1 


f 


i 


A 


14 


i 


4 


Hf 


1 


1 


1 


1 


1.31 


H 


34 


i 


3 


li 


3i 


14 


1 


f 


i 


If 


i 


1 


Iff 


lA 


i 


1 


U 


1.66 


5i 


3| 


1^ 


34 


If 


3| 


li 


4 


1 


i 


24 


A 


14 


3A 


14 


f 


2 


H 


1.9 


5f 


3i 


1 s 

TV 


3f 


If 


31 


If 


4 


1 


i 


3f 


A 


14 


Oil 


If 


f 


2 


2 


2.37 


7 


4 


1 


5 


2 


31 


14 


i 


1 


i 


3 


5 


14 


2fi 


34 


i 


2 


n 


2.87 


71 


4i 


H 


5f 


3i 


44 


If 


i 


14 


A 


3i 


f 


14 


3A 


24 


1 


2 


8 


3.5 


8^ 


5i H 


6i 


34 


5 


If 


i 


14 


5 


4 


f 


14 


m 


3i 


1 


4 


4 


4.5 


91 


641 A 


n 


3 


5i 


2 


f 


If 


A 


4i 


A 


If 


m 


44 


li 


5 


5 


5.5 


m 


7|1A 


84 


34 


7 


3i 


i 


14 


f 


6 


4 


2 


m 


5i 


It 


6 





6.62 


m 


9 


Ih 


10 


44 


8 


24 


1 


If 


1 


7 


4 


3i 


6« 


H 


u 


7 



16 



TIGHT JOINTS. 




n-y^^- ^-H 



Table of Tight Joint Flanges.— 1 ,500 lbs- Working 

Pressure. 



sis 


A 


B 


c 


D 


E 


F 


G 


H 


K 


L 


M 


N 


o 


p 


Q 


R 


Size 
of 






































Bolts 


=2 2: 

a: 


1 


.67 


3i 


If 


l"k 


2i 


1 


u 


l 


5 
Iff 


9 

Tii" 


A 


1 


i 


13 


31 
¥5 


i 


i 


1 


i 


.84 


31 


H 


ii 


2i 


li 


If 


1 


f 


1 1 

18 


A 


li 


i 


1 


lA 


f 


i 


1 


f 


1.05 


4i 


2i 


ii 


3| 




2i 


lA 


A 


f 


i 


u 


i 


1 


HI 


1 


1. 


1 


1 


1.31 


H 


Si 


11 


3i 


If 


3| 


li 


i 


1 


i 


If 


A 


H 


lit 


lA 


f 


1 


H 


1.66 


H 


3i 


H 


3t 


3 


21 


If 


i 


^ 


i 


2i 


A 


li 


2A 


H 


f 


2 


U 


1.9 


6 


3i 


1 5 
T6 


4i 


2i 


3i 


H 


i 


1 


i2| 


A 


li 


m 


If 


i 


2 


2 


2.37 


7 


4i 


ItV 


H 


H 


3f 


l| 


f 


H 


i 


3 


f 


U 


m 


2i 


1 


2 


2i 


2.87 


7f 


4f 


lA 


S| 


H 


4i 


3 


1 


li 


A 


3i 


1 


H 


3A 


n 


H 


2 



TIGHT JOINTS. 



17 



Sizes Carried in Stock for 750 lbs. Working 
Pressure. 



COUPLINGS. 


ELBOWS. 


TEES. 


FLANGE 
UNIONS. 


REDUCING 
BUSHINGS. 


i 


i 


i 





i 


f 


1- 


f 


— 


f 


i 


i 


i 


i 


i 


i 


1 


f 


f 


i 


1 


1 


1 


1 


1 


H 


li 


li 


li 


U 


U 


H 


li 


u 


H 


3 


2 


2 


2 


2 


2k 


2^ 


2^ ■ 


2^ 


3i 


3 


B 


3 


3 


3 


4 


4, 


4 


4 


4 


5 


5 


5 


5 


5 


6 


6 


6 


6 


6 



Sizes Carried in Stock for 1,500 lbs. Working 
Pressure. 



COUPLINGS. 


ELBOWS. 


TEES. 


FLANGE 

UNIONS. 


REDUCING 
BUSHINGS. 


i 


i 


i 


— 


i 


f 


f 


t 


f 


* 


* 


i 


i 


i 


i 


f 


f . 


f 


i 


i ■ 


1 


I 


1 


1 


1 


li 


li 


U 


U 


li 


n 


U 


U 


U 


U 


3 


3 


2 


2 


3 


n 


2* 


. ' n 


2i 


n 



18 



TIGHT JOINTS. 



Sizes Carried in Stock for 3,000 lbs. Working 
Pressure. 



COUPLINGS. 


ELBOWS. 
i 


TEES. 


FLANCJE 
UNIONS. 


REDUCING 
BUSHINGS. 


i 


1 
4 


i 


i 


1 


1 


1 


■ 1 


S 


i 


i 


i 


i 


i 


i 


i 


f 


f 


f 


1 


1 


1 


1 


1 


n 


U 


H 


H 


li 


u 


U 


U 


n 


u 


2 


2 


2 


— 


2 


2* 


n 


2i 


— 


- 3i 


4 


4 


4 


— 


4 




6 


6 


— 


6 



Sizes Carried in Stock for 6,000 lbs. Working 
Pressure. 



COUPLINGS. 


ELBOWS. 


TEES. 


FLANGE 
UNIONS. 


REDUCING 
BUSHINGS. 


i 


i 


4 


1. 
4 


i 


f 


t 


1 


f 


t. 


i 


i 


• i 


^ 


i 


* 


f 


f 


f 


f . 


1 


1 


1 


1 


1 


U 


li 


li 


li 


H 


li 


H 


H 


n 


H 



TIGHT JOINTS. 19 

The Reducing Bushings have the lead collar and set-screws 
the same as our regular fittings and can be supplied to meet 
any desired changes in size . 

The Flange Unions are in pairs (male and female) furnished 
complete with bolts and pure guttapercha rings. 

We can make to order Flanges and Fittings to stand any 
desired pressure. 



I 



PART 11. 



INFORMATION 

FOR USE 

IN DESIGNING HYDRAULIC PLANTS. 

COMPILED BY 

JOHN PLATT, Member of the American Societ}^ of Mechanical Engineers, 
Assoc M. Inst. C. K. 



INTRODUCTION. 



The following tables, formulae and general information have 
been compiled in the hope that they will be found of use by 
those who use hydraulic fittings and have to deal with the 
general question of hydraulic pressure transmission. 

The tables of wrought iron and steel pipe are for standard 
sizes. We have given at the head of each table pressures for 
v^hich the various thicknesses of pipe can be used. The 
makers, as a general rule, will not guarantee their pipe for 
any pressure, but pipe of a good quality from a reliable maker 
will be found to be perfectly good for the pressures stated. 

With regard to formula for thickness of hydraulic cylinders, 
considerable discretion is necessary when using any formula 
for thick, cylinders, and unl6ss those attempting to use such 
formula have considerable shop experience, we would recom- 
mend the taking of the thickness from the table used by Sir 
W. G. Armstrong. 






HYDRAULIC DATA. 



25 



Circumferences, Areas, Squares, Etc., 

Advancing by Decimals — .1 to 9.8. 



Diameter. 


Circum- 
ference . 


Area. 


Square. 


Cube. 


Square 
Koot. 


Cube 
Root. 


.1 


.814 


.00785 


.01 


.001 


.816 


.464 


.2 


.628 


.0814 




04 




008 




447 




585 


.8 


.942 


.0706 




09 




027 




548 




669 


A 


1.26 


.1256 




16 




064 




688 




787 


.5 


1.57 


.1968 




25 




125 




707 




794 


.0 


1.88 


.2827 




36 




216 




775 




843 


.7 


2.20 


.8848 




49 




848 




887 




888 


.8 


2.51 


.5026 




64 




512 




894 




928 


.9 


2.83 


.6862 




81 




729 




949 




965 


1. 


8.14 


.7854 


1 




1 












.1 


8.46 


.9508 


1 


21 


1 


33 




049 




082 


.2 


8.77 


1.181 


1 


44 


1 


73 




095 




063 


.8 


4.08 


1.827 


1 


69 


2 


20 




140 




091 


.4 


4.39 


1.539 


1 


96 


2 


74 




188 




119 


.5 


4.71 


1.767 


2 


25 


3 


37 




225 




145 


.6 


5.02 


2.011 


2 


56 


4 


10 




265 




170 


.7 


5.34 


2.270 


2 


89 


4 


91 




304 




193 


.8 


5.65 


2.545 


8 


24 


5 


83 




342 




216 


.9 


5.96 


2.835 


8 


61 


6 


86 




378 




289 


2. 


6.28 


3.142 


4 




8 






414 




260 


.1 


6.59 


3.464 


4 


41 


9 


26 




449 




281 


.2 


6.91 


3 801 


4 


84 


10 


65 




483 




301 


.3 


7.22 


4.155 


5 


29 


12 


17 




517 




820 


.4 


7.53 


4.524 


5 


76 


13 


82 




549 




339 


.5 


7.85 


4.909 


6 


25 


15 


63 




581 




357 


.6 


8.16 


5.309 


6 


76 


17 


58 




612 




375 


.7 


8.48 


5.726 


7 


29 


19 


68 




643 




392 


.8 


8.79 


6.158 


i 


84 


21 


1]5 




673 




409 


.9 


9.11 


6.605 


8 


41 


24 


.89 




708 




426 


3. 


9.42 


7.069 


9 




27 






732 




442 


.2 


10.05 


7.548 


' 10 


"24 


32 


"77 




789 


i \ 


474 


.4 


10.68 


8.558 


i M 

i 


'.56 


39 


; 30 




.844 


1 1 


'.504 



26 



HYDRAULIC DATA. 



Circumferences, Areas, Squares, Etc., 
Advancing by Decimals. .1 to 9.S. — Continued. 



Diameter. 


Circum- 
ference. 


Area. 


Square. 


Cube. 


Square 
Root. 


Cube 
Root. 


8 6 


11.80 


10.18 


12.96 


46.66 


1.897 


1.588 




8 


11.98 


11 


84 


14 


44 


54 


87 


1 . 949 




560 


4 




12.56 


12 


57 


16 




64 




2 




587 




2 


18.19 


18 


85 


17 


64 


74 


09 


2.049 




618 




4 


18.82 


15 


21 


19 


86 


85 


18 


2.098 




689 




6 


14.45 


16 


62 


21 


16 


97 


84 


2.145 




668 




8 


15.08 


18 


10 


28 


04 


110 


6 


2.191 




687 


5 




15.70 


19 


68 


25 




125 




2.286 




710 




2 


16.88 


21 


24 


27 


04 


140 


6 


2 280 




782 




4 


16.96 


22 


90 


29 


16 


157 


5 


2.824 




754 




6 


17.59 


24 


68 


81 


86 


175 


6 


2.866 




776 




8 


18 22 


26 


42 


88 


64 


195 


1 


2.408 




797 


6 




18.84 


28 


27 


86 




216 




2.449 




817 




2 


19.47 


80 


19 


88 


44 


28S 


8 


2 490 




887 




4 


20 10 


82 


17 


40 


96 


262 


1 


2.580 




857 




6 


20.78 


84 


21 


48 


56 


287 


5 • 


2 569 




876 




8 


21 86 


86 


82 


46 


24 


814 


4 


2 608 




895 


7 




21 99 


88 


48 


49 


^ 


84*8 




2 646 




918- 




2 


22 61 


40 


72 


51 


84 


878 


2 


2 688 




981 




4 


28 24 


48 


01 


54 


76 


405 


2 


' 2 720 




949 




6 


28 87 


45 


86 


57 


76 


489 




2 757 




966 




8 


24 50 


47 


78 


60 


84 


474 


6 


2 798 




988 


8 




25 18 


50 


27 


64 




512 




2 828 


2 






2 


25 76 


52 


81 


67 


24 


551 


4 


2 864 


2 


017 




4 


26 88 


55 


42 


70 


56 


592 


t 


2 898 


2 


088 




6 


27 01 


58 


09 


78 


96 


686 


1 


2 988 


2 


049 




8 


27*64 


60 


82 


77 


44 


681 


5 


2 966 


2 


065 


9 




28*27 


68 


62 


81 




729 




8 


2 


080 




2 


28*90 


66 


48 


84 


64 


778 


i 


8 088 


2 


095 




4 


29*58 


69 


40 


88 


86 


880 


6 


8 066 


2 


110 




6 


80 15 


72 


88 


92 


16 


884 


t 


8 098 


2 


125 




8 


80/78 


75 


48 


96 


04 


941 


2 


8! 180 


2 


140 



HYDRAULIC DATA. 



27 





Q 






52; 






i-H 






H 






« 






<!\ 




<D 

a 





I— 1 
m 


U4 


^ 


^ 




H 


H 


m^ 


p^ 


g 









<1) 


05 


■ Q 


C/) 


3 









'^ 









-o 


CO 


m 


c 

OS 




H 




c 


t^ 


w 





05 




L. 






■4-> 


t^ 


^ 


x: 


(/I 


H 


bfi 


H 


W 


T 


;? 


fe 





Ph 





L. 


ct 


H 


i? 


iz; 






W 


^ 




(i5 


H 











^ 






« 













^ 





Contents of 

ooe foot 
in length. 


c 






10 Oi-iO ^-^lOlO(^Dooco^ 
5Sir'^^f^ot--*QOocoo 

OOOOOOtHtHCQcOCOOIC 


T— ( 1—1 


No. of 

Threads 

per inch 

of screw. 




QO^X)'^T^'^T-lrHTHrHaOX)QOX) 


Nominal 

weight 

per foot 

of length. 


a 


Ph 


^ 10 00 ri CO CQ :o t- IC O iO t- 


tH ^ c^:j o.-? CO ic t- ^ 00 

T-H r-l T-H 


P ce 


02 

a 

a 

in 


OOiOCOOOiCOiOOOOOCOOSQO 
^THCOiOOO^OCOt-COt-OiOO 


tH GQ CO ^ L- CQ Oi 00 
T— 1 1— 1 GQ 


^ 'Jl 


«3 

a 


00 oi T-H CO ^ -* 10 ^ CO 10 00 

tH T-i tH T-H tH T-l CQ CQ O:? 0^ C^"i 




Actual 

Outside 

Diam. 


c 


'^ r- 'xt^ JO th r^ t- <© 0^ 

iOCOOOOCOOOiCOOOiOlOlOCD 


rHrH^T-HCQOlCO-T^iOCO 


l5a 


a 


<:d Oi 0^ GQ -vH 00 T-H CD G^i TiH ?o 
CO^COOOOCOOO^OOOO 


^ rH tH CQ C^-? 0? --t- iO 


Noniinal 
Inside 
Diam. 


CO 




-Hir*. :ct» He' mH< H^ ^^' '-+^' 

rH rH T-H 0? 0> CO -+ J.O CO 



28 



HYDRAULIC DATA. 







(D 



C 

o 



O 

i. 



bfi 
c 
o 

(/) 

X 



o 



CO ^, 



-a 

c 



o 
o 



c 

H 

a. 

;^ 

g 

5 

o 

o 



o 

t— I 

H 
X 

o 



c 
c 

o 



o 






Pi 
C 






o o ^ c^> r: :c; c: i^'T — ' ^ 05 T*< cC' 



O 



^|2 



eg 

■s|s" 



^ 










'"^ '^ Oi CC i- O W CQ ^- t:t t- rfH X 


fl 


iOi>OLT^OOO:CC^:»Ciii«)0 








^'i^ 


P 


^ ^ c:j :c cc ici- o T*< o x> 


^.^^10^ 



■^T— fC^'^^CrHXL'^ 



IC ^ X o ^ :c O 10 X O IC iC cc 

• ^' rH tH r-I O^' CQ CO T^* iC 5C 



05<M'^eci'ri^-ciC0'-^05T-^t-LT 

Ci '^^ LO t- C: ^7^1 T:^ C5 so X X X L- 

T-(' T-( 1-i c<i (m' CO* -Ti^ ic 



^T-rHCQC^COrJ^LOX;- 



HYDRAULIC DATA. 



29 



o 






a 


w 




a 












<i) 


H 




4-> 


< 




CO • 


P 




Ti 


CC 


o 




Ph 




c 


cc 


g 


o 


pq 





V. 


^ 


Q 


■T" 


o 


^ 


4-> 


o 


<; 




»o 




3 


o 

Eh 


h-l 


o 

5 


Ah 

J/: 


02 

< 


c 

O 


^ 
» 




(0 


Ph 


C 


cd 




PQ 


1. 

4-> 


w 


CD 


o 


H 


JD 


o 




3 


^ 




O 






Q 







o o <^ ^ 



O 



C^CiCO'^rHQOOlCCQT-IOS 

OOO^CO^OOlrHOCQ-^ 

OOOOOOOtHC^^<;00 



Nominal 
weig^ht 

per foot of 
length. 




COOOOOIOOOOOOOO 
05 IC CC -^^ O ^_ -* CO L- t- r-^ T-^ 

' ^oicO iO O Ci CO t-' 'rt^ t- S 
T-H 1-1 C.J CO lO 


t— 1 


c/1 


-^^COt-^CO^THCiO-iCOO 


tH CQ ^ i> C^i O 




CO 

o 


C^-) C5 — • O GO O ^ CO O 00 IC X 
O? O^ CO CO CO ^ ^ lO CO CO t- t- 




ill 





t- ^ lO ^ CO t- t- O O CO C^i 
CO 00 O CO CO 05 CO 00 lO lO iO CO 

* T-I tH tH i-I C'? CQ CO* tJH IC CO' 


Actual 
Inside 
Diam. 




00-^O)X00Q0CilO00COCOCO 
0"i C^ -^ lO '00 O ^_ t- G<i tH O O 

' ^ r-^ ^ cico ^ iri 




i 
■g 

c 

t-H 


tH T-H rH C^^ (7) CO ^ »C CO 



30 HYDRAULIC DATA 



Table of Tensile Strength in Pounds, 
Per Square Inch. 



Metals and Alloys. 

Brass, Cast .^ Average 18,000 

Bronze, or Gun Metal 36,000 t6 50.000 

Copper, Cast Average 19,000 

Bolts '' 36.000 

Iron. Cast. 13.500 to 29.000 " 16.500 

'• Malleable (Air furnace) 35.000 to 55.000 

'' Wrought 46,000 to 56,000 

Steel. Cast 65,000 to 85.000 

•• Crucible 90,000 to 120,000 

'' Rivet . .55,000 to 65,000 

•• Bessemer Bar 65,000 to 90.000 

Malleable iron should always be poured from the air 
furnace and made from white charcoal iron'(Nos. 3 to 5) and 
then annealed from ten to twenty days. This material can 
be used for hydraulic fittings, valves, etc., and has the tenac- 
ity given above. The so-called malleable iron, poured from 
a cupola and made of gray iron and annealed from five to ten 
days, has a tenacity of from 20.000 to 32,000 lbs. per square 
inch, and should not be used for hydraulic or machine work 



HYDRAULIC DATA. 



81 



Safe Loads for Bolts. 



Stress, 10,000 pounds per Square inch for Steel. 
7.000 •• - '^ •• - Iron. 



Diameter, 


Area at 

Bottom 

of Thread. 


Safe load in 
Sieel, 


Safe load in 
Iron. 


No, of 
Threads 
per Inch. 


i 


.126 


1.260 


.882 


18 


t 


.2i'2 


2.020 


1.414 


11 


f 


.80 


8.000 


2 . 100 


10 


i 


.42 


4.200 


2.940 


9 


1. 


.55 


5.500 


8 . 850 


8 


H 


.69 


6.900 


4.880 


7 


H 


.89 


8.900 


6.280 


7 


If 


l.oc, 


10.600 


7.420 


6 


n 


1.29 


12.900 


9.080 


6 


n 


1.51 


15 100 


10.570 


H 


If 


1.75 


17 . 500 


12.150 


5 


n 


2.05 


20.500 


14.850 


5 


2 


2.80 


28 . 000 


16.100 


4^ 


H 


8.02 


80.200 


21.140 


4^ 


H 


8.72 


87.200 


26.040 


4 



The Size of Bolt Heads and Nuts. 

Diameter of bolt = 1 . 

Diameter of head and nut, square or hexagon = Iffrom 
side to side. 

Diameter of head and nut. hexagon = 2, over angles. 
Thickness of head = f of diameter of bolt. 
Thickness of nut = diameter of bolt. 



HYDRAULIC MEMORANDA. 



A cubic foot of water contains 7.480519 gallons. 

A gallon of water contains 231 cubic inches, and weighs 
8.83111 pounds. (U. S. Standard. ) 

Tlie friction of water in pipes is as the square of the ve- 
locity. 

The height of a column of fresh water, equal to a pressure 
of one pound per square inch, is 2.31 feet. (In usual compu- 
tation this is taken at 2 feet, thus allowing for ordinary fric- 
tion . ) 

The mean pressure of the atmosphere is estimated at 14.7 
pounds per square inch, so that with a perfect vacuum it will 
sustain a column of water 33.9 feet high. 

To find the pressure in pounds, per square inch, of a column 
of water, multiply the height of the column in feet by .434 — 
Approximately we say that every foot elevation is equal to 
one-half pound pressure per square inch; this allows for ordi- 
nary friction. 

In designing hydraulic machinery, a rule should be made 
that in all cases a leather shall work against brass or hydrau- 
lic bronze, and never against cast iron. Hemp packing 
should always be used to work against iron, and not come in 
contact with brass. Hemp packing and stuffing boxes can 
readily be used, with a working pressure of 1500 lbs. per sq. in. ; 
and by the use of Du Val metallic packing in a stuffing box, 
with pressures as high as 5,000 lbs. per sq. in. 



HYDRAULIC MEMORANDA. 



m 



Working and Test Pressures. 

Working Pressure. Test Pressure. 

400 lbs . per sq. in 1 ,^50 lbs. per sq. in . 

750 '^ - " 2,000 " " 

1,500 '• " " 3,500 •• •' 

3,000 '• •' " 5,000 •' '• 

5,000 '• '' - 7,500 '• '^ 

In good practice it is always well to test the parts of all 
hydraulic machines, etc. , working at a given pressure, to the 
corresponding test pressure given in the table above. 

Table of Gallons. 



United States. 
New York. . . . 
Imperial 



Cubic 

Inches in a 

Gallon. 



231. 

221.81918 



Weight of 
a Gallon 

in Pounds 
Avoirdu- 
pois. 



8.33111 
8.00 
10.00 



Gallons in 

a Cubic 

Foot. 



7.480519 
7.901285 
6.232102 



Weight of a 
cubic foot 
of water, 
English 
standard, 
62 . 3210286 
lbs . Avoir- 
dupois. 



Useful N 


lumbers 


>■ 




Cubic Inches 


X by 


.00058 


=: 


Cubic Feet 


Circular Inches 


X ' 


.00546 


=z 


Square Feet 


Cubic Feet 


X - 


7.48 


= 


U. S. Gallons 


Cubic Inches 


X 


.004329 


zzz 


U. S. Gallons 


Cylindrical Inches 


X 


.0034 


= 


U. S. Gallons 


U. S. Gallons 


X 


.13367 


— 


Cubic Feet 


Cylin. Ft. of Water 


X 


6. 


= 


U. S. Gallons 


Cubic Ft. of Water 


X - 


62.5 


= 


Pounds Avoirdu 


Cu. In. of Water 


X 


.03617 


= 


" " [pois 


Cylin. In. of Water 


X 


.02842 


= 


.. 


268.8 U. S. Gallons of water 




— 


One Ton 


35.88 Cu. Ft. of Water 




=: 


One Ton 



84 HYDRAULIC MEMORANDA. 

Thickness of Hydraulic Cylinders.— (Formulae.) 

Merriman gives the following : 

s = allowable maximum stress in metal . 

p z= pressure in same units. 

R — outside radius. r p 

r = interior radius . t = •■ — 

t = thickness. s — p 



Rankine gives : 



^s + p 

R - ^ X r 

s — p 



The foregoing formulae apply only to ''thick cylinders," 
and must be used with discretion, as will be seen from tlie 
particulars given below. 

To bring these formulae within practical limits at all, the 
allowable maximum stress, "s," should not be taken at more 
than 4,000 lbs. per n' for the comparatively low values of 
"p," which gives "t" a value that will not make a "thick" 
cylinder. 

From a table used by Sir W. G. Armstrong, the following 
thicknesses for cast-iron cylinders for a working pressure of 
1,000 lbs. per a " are taken, and these can be relied on for 
practical work: 

Diam. of Cylinder, Inches, 2 3 4 5 6 7 
Thickness of " " 0.832, 1.042, 1.146, 1.354, 1.552, 1.77, 

Diam. of Cylinder, Inches, 8 9 10 11 12 13 
Thickness of " " 1 . 875, 1 . 979, 2 . 02, 2 . 34, 2 . 578, 2 . 734, 

Diam, of Cylinder, Inches, 14 15 16 17 18 19 
Thickness of " " 2.89,3.046,3.19,3.32, 3.45, 3.58, 

Diam. of Cylinder, Inches, 20 21 22 23 24 
Thickness of '* " 3.697,3.802,3.906,4.01,4.114 



HYDRAULIC MEMORANDA. 35 

For any other pressures, multiply by the ratio of that pres- 
sure to 1,000. 

Mr. Wm. Kent says: "These figures correspond nearly to 
the formula t — 0.175 d + 0.48, in which t = thickness, 
and d = diameter in inches up to 16 " diameter, but for 20 
inches diameter, the addition of 0.48 is reduced to 0.19, 
and at 24" it disappears." 

Cast-iron should not be used for pressures exceeding 
2,000 lbs. per d ', and it is better to use steel castings or 
forged steel for cylinders which would be over 6" thick in 
cast iron. 



36 HYDRAULir MEMORANDA. 

Capacities of Cylinders and Rams. 



Diameter. 




Load at 


C'ubic Ids. 


(lallons 


Gallons 




Area. 


1,500 lbs. 1 " 


per Foot 


per Foot 


per Incii 


Inches. 


. 7854 


in lbs. 


of Cylinder 


of Cylinder. 
.040 


of Cylinder. 


1 


1,178 


9.42 


.0038 


H 


.904^ 


1,491 


11.93 


.051 


.0042 


H 


1.227 


1,840 


14.72 


.063 


.0052 


If 


1.484 


2,227 


17.8 


.077 


. 0064 


H 


1.707 


2,650 


21.20 


.091 


.0076 


U 


2.078 


3,110 


24.87 


.107 


.0089 


If 


2.^05 


3,607 


28.86 


.124 


.0108 


u 


4,140 


33.18 


.143 


.0119 


3 


8.141 


4,711 


37.69 


.163 


.0186 


n 


3.546 


5,319 


42.55 


.184 


.0158 


n 


3.976 


5,964 


47.71 


.206 


. .0171 


n 


4.430 


6,645 


53.16 


.280 


.0191 


n 


4.908 


7,862 


58.90 ■ 


.254 


.0211 


H 


5.411 


8,116 


64.98 


.281 


.0234 


2f 


5.939 


8,908 


71.26 


.308 


.0257 


2* 


6.491 


9.786 


77.89 


. .887 


.0281 


a 


7.068 


10,602 


84.81 


. 367 


.0306 


H 


8.295 


12442 


99.5.4 


.430 


.0858 


■n 


9.621 


14,481 


115.45 


.50 


.0416 


n 


11.04 


16.560 


183.48 


.573 


. 0477 


4 


12.56 


18,840 


150.72 


'652 


.0543 


H 


14.18 


21.270 


169.92 


.785 


.0612 


H 


15.90 


23.850 


190.80 


.826 


.0688 


4f 


17.72 


26,580 


212.64 


.920 


.0767 


5 


19.68 


29,445 


285.56 


1.02 


.0850 


H 


21.64 


32,460 


259.68 


1.124 


.0936 


5+ 


28.75 


35,625 


285.0 


1.28 


. 1025 


.">* 


25.96 


38,940 


811.52 


1.348 


.1123 


6 


88.27 


42,405 


339.24 


1.468 


.122 


H 


80.67 


46,005 


368.04 


1-59 


. 132 


(i.V 


83.18 


49.770 


398.16 


1.72 


.143 


<if 


35.78 


53.670 


429.36 


1 1.85 


. 154 


T 


38.48 


57,720 


461.76 


i 1.99 


.165 


u 


41.28 


61,920 


495.36 


2.14 


.178 


7i 


44.17 


66,255 


530.04 


2.29 


.190 



HYDRAULIC MEMORANDA. B7 

Capacities of Cylinders and Ra.Yns.— Continued. 



Diameter. 




Load at 


Cubic Ins 


Gallons 


Gallons 




Area 


1,500 lbs a " 


per Foot 


per Foot 


per Inch 


Inches. 




in lbs. 


of Cylinder. 


of Cylinder. 


of Cylinder'. 


n 


47.17 


70,755 


566.04 


2 45 


.20 


8 


50.26 


75,390 


603.12 


2.61 


.217 


H 


53.45 


80,175 


641.40 


2.77 


.230 


8i 


56.74 


85,110 


680.88 


2 94 


.245 


8f 


60.13 


90,195 


721.56 


8.12 


.260 


9 


63 . 61 


95,415 


768.32 


3.80 


.275 


Qi 


67.20 


100,800 


806.40 


3.49 


.290 


H 


70 88 


106,320 


850.56 


3.68 


.806 


n 


74 66 


111,990 


895.92 


3.87 


322 


10 


78.54 


117,810 


942.48 


4 08 


JS40 


10^ 


86.59 


129,885 


1039.0 


4.50 


. 875 


11 


95.08 


142,545 


1140.8 


4.93 


.410 


lU 


103.8 


155.700 


1245.6 


5.39 


.449 


12 


118.0 


169.500 


1856.0 


5.87 


.489 


12^ 


122.7 


184,050 


1472.4 


6,87 


.530 


18 


182.7 


190,050 


1592.4 


6.89 


. 574 


Vdk 


148.1 


214.650 


1717.2 


7.48 


.619 


14 


158 . 9 


230,850 


1846.8 


8.00 


.666 


14^ 


. 165.1 


247.650 


1981.2 


8.57 


.714 


15 


176.7 


265.050 


2120.4 


9.17 


.764 


I'H 


188.6 


282.900 


2263.2 


9.80 


.816 


16 


201.0 


301,500 


2412.0 


10 44 


.87 


16^ 


213 8 


320,700 


2565.6 


11.10 


.925 


17 


226.9 


340.850 


2722.8 


1 1 . 78 


.981 


in 


240.5 


360,750 


2886.0 


12.49 


1 .04 


18 


254.4 


381,600 


3052.8 


13.21 


1.10 


18i 


268.8 


403.200 


3225.6 


13.96 


1.16 


19 


288.5 


425,250 


3402.0 


14.72 


1.22 


19i 


298.6 


447,900 


3583.2 


1^51 


1 .29 


^20 


314.1 


471,150 


3769.2 


16.81 


1.36 



HYDRAULIC PRESSURE 
TRANSMISSION. 



INTRODUCTION. 

Water under high pressure (700 lbs. per z and upward,) 
affords] a ready and satisfactory method of transmitting power 
to a distance, and is particularly adapted to the movement of 
heavy loads at moderate velocities, by cranes and elevators . 
It is also the most efl&cient way of operating large tools for 
pressing and joining metals, as in riveting, flanging, punch 
ing, shearing, forging and also for the operation of turret- 
in battle ships, and of disappearing gun carriages, high duty 
elevator plants, etc. , etc. 

That it can be made to operate tools quickly is shown 
from the fact that forging presses are now made to make from 
50 to 60 strokes per minute. The system usually consists of 
one or more pumps, capable of developing the required 
pressure: accumulators, which are vertical- cylinders with 
heavily weighted plungers passing through stuffing boxes, by 
which a quantity of water may be accumulated at the pressure 
to which the plunger is weighte<:l: and of the distributing 
mains to the presses, cranes or other machinery to be operated. 

MECHAXICAL VALUE OF WATER rXDEE 
ACCUMULATOR PRESSURE. 

TJie gross amount of energy of the water under pressure 
(stored in the accumulator.) measured in foot poimds, is its 
volume in cubic feet X its pressure in pounds per square foot. 
The horse power of a given quantity, steadily flowing, is 



HYDRAULIC PRESSURE TRANSMISSION. 39 

144 p Q 

H. p. =r ^ .2618 p Q 

550 
in which Q = quanity flowing in feet per second, 
and p = j)ressure in pounds per square inch. 
Theoretically, the mechanical value of water under an 
accumulator pressure of 700 lbs. per n " (549.78 per circu- 
lar inch), is 100,800 foot lbs., or 45 foot tons pea- cubic foot of 
water, irrespective of the time in which it is consumed. 
This gives 3.0545 H. P. per cu. ft. per minute, or one H. P. 
requires 0.32738 per cu. ft per minute. Approximately, this 
equals 1 H. P. from 2 gallons of water, but practically, allow- 
ing for all losses, 3^ gallons are required. 

THE EFFICIENCY OF HYDRAULIC APPARATUS. 

The useful effect of a direct acting cylinder, ram or 
plunger is usually taken at 93 per cent. , though in practice 
it is found that the friction loss varies from 5 per cent, to 
18 per cent, according to the condition of the packing, 
which makes the Armstrong practice of 86 per cent, safer 
to use in ordinary work. The folio wing table is given by 
Mr. Percy Westmacott as the efficiency of a ram with 
chain and pulley multiplying gear, properly proportioned 
sxidi well lubricated. 

Multiplying 

2 to 1 4 to 1 6 to 1 8 to 1 10 to 1 12 to 1 14 to 1 16 to 1 
Efficiency, per cent. 

80 72 72 67 63 59 54 50 

With large sheaves, small steel pins and wire rope, the 
efficiency has been found as high as 66 per cent, for a 
multiplying power of 20 to 1. 

Henry Adams gives the following formula for effective 
pressures in cranes and hoists ; it will be found to correspond 
with the above. 



40 HYDRAULIC PRESSURE TRANSMISSION. 

P = Accumulator pressure in lbs. per d" 
m = ratio of multiplying power. 

E = effective power in lbs. per z\ including all allow ^ 
ances for friction. 

E = P (.84 — .02 m) 

SPEED OF HOISTING BY HYDRAULIC POWER. 

The maximum allowable speed for warehouse cranes is 6- 
ft. per second; for platform cranes and lifts, 4 ft. per second; 
for passenger and wagon hoists with heavy loads. 2 feet per 
second. Mr. Henry Adams is authority for the statement that 
••The maximum speed under any circumstances should never 
exceed 600 ft. per minute.' But recent elevator practice haa 
shown that a speed of from TOO to 800 ft. per minute can be 
attained . 

VELOCITY OF ^VATER THROUGH PIPES 
AXD VALVES. 

The following table gives the velocity in feet per second at 
pressures from 700 lbs. to 5.000 lbs. . which the water will ac- 
quire if discharged into the atmosphere through an approx- 
imately frictionless aperture. Velocities for intermediate 
pressures may be calculated from the formula: — 

Velocity in feet per second = r2.19 v' pressure in lbs. = '. 



Iq lbs. Pressure per 
Square Inch. 


700 


1500 


2000 


3000 


4000 


5000 


Velocity in feet per 
second 


326 


472 


548 


670 


772 


862 



With an accumulator pressure of 700 lbs. per z the natural 
velocity (theoretically) is 326 ft . per second . It is found in 



HYDRAULIC PRESSURE TRANSMISSION. 41 

practice that not more than one-tenth of this can be obtained 
through the pipes and one third through the valves, in order 
to maintain the proper speed of the machinery. The loss 
from friction in the pipes is about 1 lb. per n " per 100 feet in 
length, after they have been laid some time, 1 lb. additional 
for each bend, and 10 lbs. for each branch. It is usual in cal- 
culating to take the speed of the water through valves at not 
more than 98 feet per second . 

Experiments with water at 1600 lbs. per n " flowing into 
a flanging press cylinder 20" diameter, through a i" pipe con- 
tracted at one point to i", gave a velocity of 114 feet per second 
in the pipe, and 456 feet at the reduced section. Through a 
i" pipe reduced to f" at one point, the velocity was 213 feet 
per second in the pipe, and 381 at the reduced section. In a ^ 
inch pipe without contraction, the velocity was 355 feet per 
second. 

AREAS OF VALVES FOR MACHINERY UNDER 
ACCUMULATOR PRESSURE.— (Formvi^af..) 

A = Area of lifting ram. 

m =r Ratio of multiplying power. 

V = Velocity of load in feet per second. 

V = " " water through valve in feet per second. 
W = Length of ram, cross-head, sheaves, chain, etc., in lbs. 
a = Area of lifting valve (mitred spindle) . 

a' = " " lowering " " " 

A V A V 



m V m V^ 13 8 W 

When cylinder is horizontal, then A 

W 

= area of returning ram. 

700 



42 HYDRAULIC PRESSURE TRANSMISSION. 

AREA OF PORTS IN SLIDE F^LFE-^.— (Formulae.) 

(V-SHAPED OPENINGS.) 

V = velocity of load in feet per second, 
m -— Multiplying power . 
A = Area of ram in n " 

A V 
Area of pressure port = 



Area of exhaust port = 



m 
1.5 A V 



ra 



LIFTING RAMS FOR HYDRAULIC CRANES.- 

(FORMULAE. ) 

W = Load to be lifted in pounds . 

w = Weight of ram, cross-head, chain or sheaves. 

1 = Height of lift in feet. 

m = Multiplying power. 

e = Coefficient of effect = (.84 — .02 m) 

a = Area of ram in n " 

p = Accumulator pressure in lbs. per d " 

W m 
For horizontal cvlinders : a 



vertical 





p 


c 




w 


m 


+ 


w 




P 


c 




w 


m 


— 


w 



Inverted '* a, — 

P c 



HYDRAULIC PRESSURE TRANSMISSION. 43 

TURNING RAMS FOR HYDRAULIC CRANES.— 
(Formulae.) 
w = load in tons, 
k = rake in foot 

1 = length between bearings in feet, 
d = diameter turning drum in feet, 
p = accumulator pressure in lbs. per a " 
m = multiplying power, (usually 2 to 1 . ) 
a = area turning ram per d " 
f — a constant. 

W R 2 f m 

a = 

1 d p 

f = 70 for cranes up to li tons 
f =r 60 *• " " '^ 4 " 
f = 50 " '^ " " 10 ^' 



INDEX. 

PAGE. 

Armstrong Standard Flange Joint 1^ 

Armstrong's Table of Hydraulic Cylinder Thicknesses 34 

American Tract Society Building Elevator Plant 9 

Atmospheric Pressure. 32 

Accumulators 38 

Allowable Speed of Cranes, Lifts, Etc. , 40 

Areas of Valves (Mitre Seat) 41 

" Ports in Slide Valves 42 

Areas, Table of 25, 26 

Brass, Tensile Strength of 30 

Bronze, " '' " 30 

Bessemer Bar Steel, Tensile Strength of 30- 

Bushings, Eeducing 18 

Bolts, Safe Loads for 31 

'' Copper, Cast, Tensile Strength of 30 

Box, Stuffing 32 

Castings (Steel), Tensile Strength of 30 

Cast Steel '' " '' 30 

•' Iron " '' '' 30 

Crucible Steel '' '' '' 30 

Cupola, Malleable Iron from " " 30 

Copper Bolts, Cast '' " '^ 30 

Circumferences, Table of 25, 26 

Cylinders, Thickness of Hydraulic 34 

Capacities of Rams 36, 37 

Cranes, Speed of Warehouse and Platform. 40 

" Lifting Rams for 42 

' ' Turning Rams for 43 

Collar, Lead Collar in Joint 8, 9 

Cubes, Table of 25, 26 

Du Val, Metallic Packing 32 

Energy of Water Under Pressure 38 

Efficiency of Rams 39 

" Multiplying Gear 39 

* ' Rams with Wire Rope . , 39 

Elevators. Passenger 38 

Otis 9 

Flanging Press 41 



46 INDEX. 

PAGE. 

Flange Unions 13 

Flanges. Table of 750 lbs 15 

'' 1.500 lbs 16 

Forged Steel. Tensile Strength of 80 

Friction of Water in Pipe 41 

' ' Loss from . 41 

Fittings, 3.000 and 5.000 lbs 18 

' • Size of 750 lb 17 

'• '' 1,5001b 17 

Guttapercha Ring 13 

Gear, Efficiency of Multiplying 39 

Gallons, Table of 33 

Hydraulic Cylinders. Thickness of 34 

' ' Memoranda 32 

• • Pressure Transmission 38 

Hemp Packing 32 

H. P. Water Under Pressure 39 

Hoisting. Speed of 40 

Hoists, Wagon ' ' " 40 

Iron, Cast, Tensile Strength 30 



Malleable, 
Wrought, 
Pipe 



30 
30 
30 



Jacobus, Prof. D. S., Report , 12 

Joint. Leather 14 

Guttapercha 13 

'• Flange 13 

Kent, William 3, 35 

Loss from Friction 41 

' ' in Valves 41 

' ' in Pipes 41 

Lifting Rams for Cranes 42 

Lead Collar in Joint 8, 9 

Leather Joint 14 

Leathers 32 

Loads for Bolts, Safe 31 

Multiplying Gear, Efficiency of 39 



INDEX. 47 

PAGE 

Metallic Packing, Du VaL 82 

Malleable Iron Air Furnace 80 

" ' • from Cupola. ,.....; HO 

Memoranda. Hydraulic 32 

Merriman's Formula for Thickness Hydraulic Cylinders . . 34 

Numbers, Useful. 38 

Otis Elevator Plant. 9, 10, 11 

Ordinary Pipe Sizes 27 

Passenger Elevators. 88 

Pressure Transmission, Hydraulic 38 

Under Water 88 

' ' Atmospheric 82 

Pressures, Working and Test 38 

Press, Flanging 41 

Platform Cranes 40 

Packing Leathers 82 

Hemp 32 

Du Val Metallic 32 

Pipe, Wrought Iron 27 

" Steel 28 

" Friction of Water in 41 

' ' Ordinary 27 

' ' Loss from Friction in 41 

" X Strong 28 

'' XX - 29 

Recess for Lead 8 

Reducing Bushings 18 

Report, Jacobus 12 

Rankin's Formula for Thickness of Hydraulic Cylinders. J^4 

Rams, Lifting for Cranes 42 

' ' Turning " " 48 

' ' Capacities of 86, 87. 

" Efficiency of 89 

Ring, Guttapercha 18 

Rope (Wire), Efficiency with 89 

Rivet Steel, Tensile Strength of 30 

Size of Fittings. 750 lbs 17 

" " '' 1,500 '' 17 

Stock of Fittings l-"). 16, 1 7, 18 



48 INDEX. 

PAGE. 

Steel. Tensile Strength of Forged Steel 30 

'' Pipe, '^ " '' 28 

'' Cast, '' " '* 30 

'' Rivet, '' '' " 30 

' ' Bessemer Bar, Tensile Strength of 30 

" Castings, " " '' 30 

Safe Loads for Bolts ." 31 

Squares, Table of 25, 26 

Strength. Table of Tensile Strength 30 

Stuffing Box 82 

Speed of Hoisting 40 

" Allowable 40 

Table of Flanges, 750 lbs 15 

" " '' 1,500 " 16 

-' " Hydraulic Cylinder Thicknesses. Armstrong's. . . 34 

" ^' Gallons 33 

'^ Tensile Strength 30 

Tensile Strength, Table of 30 

Thickness of Hydraulic Cylinders 34 

Tract Society Building Elevator Plant , . . .9, 10, 11 

Test and Working Pressures .' 33 

Turning Rams for Cranes 43 

Unions, Flange ; 13 

Useful Numbers 33 

Velocity of Water .*....... 40 

Valves, Loss from Friction in 41 

' ' Area of 41 

' ' Areas of Port and Slide 4:^ 

Water, Velocity of 40 

' ' in Pipe, Friction of 40 

' ' Under Pressui'e 38 

Wire Rope, Efficiency with. 39 

Wagon Hoists 40 

Wrought Iron Pipe 27, 28, 29 

Wrought Iron, Tensile Strength of 30 

Working and Test Pressures 33 

Warehouse Cranes, Platform 40 

William Kent 3, 35 

X Strong Pipe, Table of Sizes 28 

XX '' " ^' " " 29 



cc 



Tk^i^I' joiiVT" 



Ammonia, Steam and Compressed Air Fittings. 




A complete line of Elbows, Tees, Couplings, Return Bends, 

Flange Unions, Reducing Fittings and Bushings 

carried in stock. 

Wii.1, Not Leak From KxpaNvSion and Contraction. 

TIGHT JOINT COMPANY, 

159-161 BANK STREET, NEW YORK. 



97 Cedar Street, New York City, 

CONSULTING HYDRAULIC ENGINEERS. 

Special attention paid to the laying out and piping up of 
Hydraulic and High Pressure Systems. 



r 



^1 ^wiMvjncoo 



021 218 343 A 




